JPWO2018003121A1 - Heat exchanger and refrigeration cycle apparatus equipped with the heat exchanger - Google Patents

Abstract

The heat exchanger includes a plate-like fin and a plurality of heat transfer tubes mounted so as to intersect the fin, the heat transfer tubes being arranged at intervals in the long side direction of the fin, and the fin is at least A part thereof has a corrugated shape and can be expanded and contracted in the long side direction.

Description

  The present invention relates to a heat exchanger including a flat heat transfer tube, and a refrigeration cycle apparatus including the heat exchanger.

  In recent years, heat exchangers using flat multi-hole tubes made of aluminum have been used for car air conditioners or stationary air conditioners. A flat multi-hole tube is a heat transfer tube having a shape in which the width (cross-sectional major axis direction) is larger than the vertical width (cross-sectional minor axis direction), and a plurality of fluid flow paths are formed therein. . Corrugated fins are generally used in heat exchangers using flat multi-hole tubes, but recently plate-type fins have also been used. Hereinafter, a heat exchanger using a flat multi-hole tube and a plate type fin is referred to as a fin tube type heat exchanger.

  A fin-tube heat exchanger is generally configured by directly inserting a heat transfer tube formed of a flat multi-hole tube into an aluminum header disposed at an end of the heat exchanger. In addition, the plate fin is provided with a recess having substantially the same shape as the cross-sectional shape of the flat multi-hole tube. By inserting the flat multi-hole tube into the recess from the width direction of the fin, a fin tube heat exchanger is manufactured. . And the construction method which brazes a heat exchanger tube, a fin, and a header simultaneously in a furnace is generally adopted.

  As a conventional fin tube type heat exchanger, there exists a thing of a structure as disclosed by patent document 1, for example. The fin tube type heat exchanger disclosed in Patent Document 1 inserts a heat transfer tube configured as a flat multi-hole tube into a tube insertion portion having a shape similar to the shape of the heat transfer tube formed on the fin from its side surface. Thus, a structure is adopted in which the joint surfaces of both are brought into close contact by a method such as brazing.

JP2015-132468A

However, generally, when producing a fin tube type heat exchanger, it is necessary to simultaneously insert fins into a large number of heat transfer tubes. Therefore, in the method disclosed in Patent Document 1, if there is a displacement between the fins and the heat transfer tubes, an excessive force is generated to insert a large number of heat transfer tubes, and insertion failure or fin bending, etc. Could occur.
Moreover, in order to prevent the position shift of a fin and a heat exchanger tube, the method of expanding the clearance gap between the tube insertion part provided in the fin and the heat exchanger tube can be considered. However, when the gap between the tube insertion portion and the heat transfer tube is enlarged, the brazing property between the fin and the heat transfer tube is deteriorated, and there are problems such as deterioration of adhesion and increase in the amount of brazing material used.

Moreover, in order to prevent the position shift of the position of a fin and a heat exchanger tube by the thermal expansion difference, exact | strict temperature control was also required. For example, the linear expansion coefficient of aluminum is about 23 × 10 ⁻⁶ , and the linear expansion coefficient of iron is about 12 × 10 ⁻⁶ . Therefore, for example, the height of the heat exchanger tubes and fins made of aluminum is 1 m in the step direction, the jig for aligning the heat exchanger tubes is made of iron, and the temperature difference in the work space between summer and winter is 20 deg. Assuming that there is a dimensional deviation due to the difference in linear expansion coefficient between aluminum and iron with respect to the length of 1 m in height of the heat exchanger, 0.26 mm will occur.

  The present invention has been made to solve the above-described problems, and enables the pitch of the tube insertion portion formed in the fin to be adjusted to the pitch of the heat transfer tube mounting portion of the header into which the heat transfer tube is inserted. The present invention provides a heat exchanger with improved assemblability and a refrigeration cycle apparatus including the heat exchanger.

  The heat exchanger according to the present invention includes plate-like fins and a plurality of heat transfer tubes mounted so as to intersect the fins, and the heat transfer tubes are spaced apart in the long side direction of the fins. The fins are arranged such that at least a part of the fins has a corrugated shape and can be expanded and contracted in the long side direction.

  The refrigeration cycle apparatus according to the present invention includes a refrigerant circuit in which a compressor, a first heat exchanger, a throttling device, and a second heat exchanger are connected by a refrigerant pipe, and the heat exchanger is connected to the first heat exchange. And at least one of the second heat exchanger.

In the heat exchanger according to the present invention, at least a part of the fin has a corrugated shape and can be expanded and contracted in the longitudinal direction of the fin, so that the pitch of the fin tube insertion portion can be automatically adjusted. Therefore, according to the heat exchanger which concerns on this invention, the assembly property of a heat exchanger can be improved.
Further, according to the refrigeration cycle apparatus according to the present invention, the above heat exchanger is used as at least one of the first heat exchanger and the second heat exchanger, so that the assemblability is improved accordingly. Become.

It is a schematic block diagram which shows an example of the refrigerant circuit structure of the air conditioning apparatus which concerns on Embodiment 1 of this invention. It is a perspective schematic diagram which shows an example of the external appearance structure of the heat exchanger which concerns on Embodiment 2 of this invention. It is a side view which shows an example of a structure of the heat exchanger which concerns on Embodiment 2 of this invention. It is a schematic sectional drawing which shows the cross section of the heat exchanger tube which comprises the heat exchanger which concerns on Embodiment 2 of this invention. It is a side view which shows the state which looked at the example of the structure of the heat exchanger which concerns on Embodiment 2 of this invention from another direction. It is a block diagram which shows an example of the specific structural example of the fin which comprises the heat exchanger which concerns on Embodiment 2 of this invention. It is a side view which shows the state which looked at another example of the structure of the heat exchanger which concerns on Embodiment 2 of this invention from another direction. It is a block diagram which shows another example of the specific structural example of the fin which comprises the heat exchanger which concerns on Embodiment 2 of this invention. It is a side view which shows the state which looked at another example of the structure of the heat exchanger which concerns on Embodiment 2 of this invention from another direction. It is a block diagram which shows another example of the specific structural example of the fin which comprises the heat exchanger which concerns on Embodiment 2 of this invention.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings as appropriate. In addition, in the following drawings including FIG. 1, the relationship of the size of each component may be different from the actual one. Further, in the following drawings including FIG. 1, the same reference numerals denote the same or equivalent parts, and this is common throughout the entire specification. Furthermore, the forms of the constituent elements shown in the entire specification are merely examples, and are not limited to these descriptions.

Embodiment 1 FIG.
First, the air conditioning apparatus 100 according to Embodiment 1 of the present invention will be described. FIG. 1 is a schematic configuration diagram illustrating an example of a refrigerant circuit configuration of the air-conditioning apparatus 100. In FIG. 1, the refrigerant flow during the cooling operation is indicated by a broken line arrow, and the refrigerant flow during the heating operation is indicated by a solid line arrow. The air conditioner 100 is an example of a refrigeration cycle apparatus. Moreover, the air conditioning apparatus 100 shall be provided with the heat exchanger which concerns on Embodiment 2 of this invention demonstrated in detail below.

<Configuration of Air Conditioner 100>
As shown in FIG. 1, the air conditioner 100 includes a compressor 101, a first heat exchanger 102, a first fan 105, a throttle device 103, a second heat exchanger 104, a second fan 106, and a flow path switching. A device 107 is provided. The compressor 101, the 1st heat exchanger 102, the expansion apparatus 103, the 2nd heat exchanger 104, and the flow-path switching apparatus 107 are connected by the refrigerant | coolant piping 110, and the refrigerant circuit is formed.

  The compressor 101 compresses the refrigerant. The refrigerant compressed by the compressor 101 is discharged and sent to the flow path switching device 107. The compressor 101 can be composed of, for example, a rotary compressor, a scroll compressor, a screw compressor, a reciprocating compressor, or the like.

  The first heat exchanger 102 functions as a condenser during heating operation and functions as an evaporator during cooling operation. The first heat exchanger 102 is, for example, a finned tube heat exchanger, a microchannel heat exchanger, a shell and tube heat exchanger, a heat pipe heat exchanger, a double tube heat exchanger, or a plate heat exchanger. Or the like. In addition, when applying the heat exchanger which concerns on Embodiment 2 as the 1st heat exchanger 102, the 1st heat exchanger 102 will be referred to as a fin tube type heat exchanger.

  The expansion device 103 expands and depressurizes the refrigerant that has passed through the first heat exchanger 102 or the second heat exchanger 104. The expansion device 103 may be constituted by, for example, an electric expansion valve that can adjust the flow rate of the refrigerant. In addition, as the expansion device 103, not only an electric expansion valve but also a mechanical expansion valve employing a diaphragm for a pressure receiving portion, a capillary tube, or the like can be applied.

  The second heat exchanger 104 functions as an evaporator during heating operation and functions as a condenser during cooling operation. The first heat exchanger 102 is, for example, a finned tube heat exchanger, a microchannel heat exchanger, a shell and tube heat exchanger, a heat pipe heat exchanger, a double tube heat exchanger, or a plate heat exchanger. Or the like. In addition, when applying the heat exchanger which concerns on Embodiment 2 as the 2nd heat exchanger 104, the 2nd heat exchanger 104 will be called a finned tube heat exchanger.

  The flow path switching device 107 switches the refrigerant flow between the heating operation and the cooling operation. That is, the flow path switching device 107 is switched so as to connect the compressor 101 and the first heat exchanger 102 during the heating operation, and switched so as to connect the compressor and the second heat exchanger 104 during the cooling operation. It is done. Note that the flow path switching device 107 may be constituted by a four-way valve, for example. However, a combination of a two-way valve or a three-way valve may be adopted as the flow path switching device 107.

The first fan 105 is attached to the first heat exchanger 102 and supplies air, which is a heat exchange fluid, to the first heat exchanger 102.
The second fan 106 is attached to the second heat exchanger 104 and supplies air as a heat exchange fluid to the second heat exchanger 104.

<Operation of Air Conditioner 100>
Next, operation | movement of the air conditioning apparatus 100 is demonstrated with the flow of a refrigerant | coolant. Here, the operation of the air conditioner 100 will be described by taking as an example a case where the heat exchange fluid is air and the heat exchange fluid is a refrigerant. The operation of the air conditioner 100 will be described on the assumption that the first heat exchanger 102 cools or heats the air in the air-conditioning target space. In addition, the flow of the refrigerant at the time of the cooling operation is indicated by a broken line arrow in FIG. Further, the flow of the refrigerant during the heating operation is indicated by solid line arrows in FIG.

First, the cooling operation performed by the air conditioner 100 will be described.
As shown in FIG. 1, by driving the compressor 101, high-temperature and high-pressure gaseous refrigerant is discharged from the compressor 101. Hereinafter, the refrigerant flows according to the broken line arrows. The high-temperature and high-pressure gas refrigerant (single phase) discharged from the compressor 101 flows into the second heat exchanger 104 functioning as a condenser via the flow path switching device 107. In the second heat exchanger 104, heat exchange is performed between the flowing high-temperature and high-pressure gas refrigerant and the air supplied by the second fan 106, and the high-temperature and high-pressure gas refrigerant is condensed to a high-pressure liquid. Refrigerant (single phase).

  The high-pressure liquid refrigerant sent out from the second heat exchanger 104 becomes a two-phase refrigerant consisting of a low-pressure gas refrigerant and a liquid refrigerant by the expansion device 103. The two-phase refrigerant flows into the first heat exchanger 102 that functions as an evaporator. In the first heat exchanger 102, heat exchange is performed between the flowing two-phase refrigerant and the air supplied by the first fan 105, and the liquid refrigerant of the two-phase refrigerant evaporates. It becomes a low-pressure gas refrigerant (single phase). The air-conditioning target space is cooled by this heat exchange.

  The low-pressure gas refrigerant sent out from the first heat exchanger 102 flows into the compressor 101 via the flow path switching device 107, is compressed to become a high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 101 again. Thereafter, this cycle is repeated.

Next, the heating operation which the air conditioning apparatus 100 performs is demonstrated.
As shown in FIG. 1, by driving the compressor 101, high-temperature and high-pressure gaseous refrigerant is discharged from the compressor 101. Hereinafter, the refrigerant flows according to solid arrows. The high-temperature and high-pressure gas refrigerant (single phase) discharged from the compressor 101 flows into the first heat exchanger 102 functioning as a condenser via the flow path switching device 107. In the first heat exchanger 102, heat exchange is performed between the flowing high-temperature and high-pressure gas refrigerant and the air supplied by the first fan 105, and the high-temperature and high-pressure gas refrigerant is condensed to a high-pressure liquid. Refrigerant (single phase). The air-conditioning target space is heated by this heat exchange.

  The high-pressure liquid refrigerant sent out from the first heat exchanger 102 becomes a two-phase refrigerant consisting of a low-pressure gas refrigerant and a liquid refrigerant by the expansion device 103. The two-phase refrigerant flows into the second heat exchanger 104 that functions as an evaporator. In the second heat exchanger 104, heat exchange is performed between the flowing two-phase refrigerant and the air supplied by the second fan 106, and the liquid refrigerant of the two-phase refrigerant evaporates. It becomes a low-pressure gas refrigerant (single phase).

  The low-pressure gas refrigerant sent out from the second heat exchanger 104 flows into the compressor 101 via the flow path switching device 107, is compressed to become a high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 101 again. Thereafter, this cycle is repeated.

Embodiment 2. FIG.
FIG. 2 is a schematic perspective view showing an example of an external configuration of a heat exchanger (hereinafter referred to as a heat exchanger 150) according to Embodiment 2 of the present invention. FIG. 3 is a side view showing an example of the configuration of the heat exchanger 150. Based on FIG.2 and FIG.3, the heat exchanger 150 is demonstrated. Here, the case where the heat exchanger 150 is applied as the second heat exchanger 104 of the air-conditioning apparatus 100 according to Embodiment 1 will be described as an example. However, the heat exchanger 150 may be applied as the first heat exchanger 102 of the air conditioner 100 or may be applied to any of them.

  As shown in FIG. 2, the heat exchanger 150 is a two-row heat exchanger, and the windward side heat exchanger 151, the leeward side heat exchanger 152, the windward side header collecting pipe 153, and the leeward side header collecting pipe 154. The inter-row connecting member 155 is constituted. In addition, the windward side heat exchanger 151 and the leeward side heat exchanger 152 are configured similarly. In the following description, when the heat exchanger 150 is described, both the windward side heat exchanger 151 and the leeward side heat exchanger 152 are described.

  Further, as shown in FIG. 2, the windward header collecting pipe 153 and the leeward header collecting pipe 154 are indicated by white arrows on the right side of the drawing with respect to the windward heat exchanger 151 and the leeward heat exchanger 152. Attached to. Further, as shown in FIG. 2, the inter-row connecting member 155 is attached to the windward side heat exchanger 151 and the leeward side heat exchanger 152 as indicated by white arrows from the left side of the drawing. In this way, the heat exchanger 150 is manufactured. In addition, the windward side heat exchanger 151 and the leeward side heat exchanger 152 are comprised similarly.

  In the windward header collecting pipe 153, a plurality of pipe attachment portions 153a to which the heat transfer tubes 2 are attached are formed. Similarly, in the leeward header collecting pipe 154, a plurality of opening portions 154a to which the heat transfer tubes 2 are attached are formed. The distance between adjacent pipe attachment portions 153a of the windward header collecting pipe 153 is defined as a pitch P1. Similarly, the windward header collecting pipe 153 is formed so that the pipe mounting portions 154a are adjacent to each other at P1.

  As shown in FIGS. 2 and 3, the heat exchanger 150 includes a plurality of rectangular plate-like fins 1 having a long side and a short side, and a plurality of heat transfer tubes 2. In addition, in FIG. 3, the case where the number of the heat exchanger tubes 2 is eight is shown as an example. As shown in FIG. 3, the distance between the adjacent tube insertion portions 5 of the fins 1 is defined as a pitch P2. The symbols shown in FIGS. 1 to 3 are similarly used in the following drawings. Moreover, in the following description, the long side direction of the fin 1 is referred to as the long side direction, and the short side direction is referred to as the short side direction.

(Schematic configuration of heat transfer tube 2)
FIG. 4 is a schematic cross-sectional view showing a cross section of the heat transfer tube constituting the heat exchanger 150. Based on FIG. 4, the heat exchanger tube 2 which comprises the heat exchanger 150 is demonstrated in detail.

  The plurality of heat transfer tubes 2 are attached to the plurality of tube insertion portions 5 formed on the fin 1 and intersect the fin 1. As shown in FIG. 4, the heat transfer tube 2 is configured in a shape in which the lateral width (cross-sectional major axis direction) is larger than the vertical width (cross-sectional minor axis direction). That is, the plurality of heat transfer tubes 2 are arranged such that the direction of the major axis of the cross section is the flow direction of the fluid flowing between the fins 1 and spaced in the step direction (vertical direction in the drawing) perpendicular to the flow direction. . In the following description, the major section of the heat transfer tube 2, that is, the portion extending in the width direction (short direction) of the fin 1 may be referred to as the width direction of the heat transfer tube 2.

  The heat transfer tube 2 shown in FIG. 4 will be described as an example where the heat transfer tube 2 is a flat tube having a flat shape with a width (cross-sectional major axis direction) larger than a vertical width (cross-sectional minor axis direction). It is not necessary to be configured in a flat shape, and the heat transfer tube 2 only needs to have a shape in which the horizontal width is larger than the vertical width.

  As shown in FIG. 4, the heat transfer tube 2 includes an upper surface 2 a including an upper portion, a lower surface 2 c including a lower portion, one side portion 2 b including one end portion in the width direction (the end portion on the right side in FIG. 4), and The other side portion 2d including the other end portion in the width direction (the end portion on the left side in FIG. 4) is provided. 4 shows an example of the heat transfer tube 2 in which the upper surface 2a and the lower surface 2c are parallel, but at least one of the upper surface 2a and the lower surface 2c is inclined so that the upper surface 2a and the lower surface 2c are parallel. It does not have to be.

The cross-sectional shape of each of the one side portion 2b and the other side portion 2d is an arc shape. In a state where the heat transfer tube 2 is mounted on the tube insertion portion 5 of the fin 1, the other side portion 2 d is located on the back portion 5 b side of the tube insertion portion 5 formed on the fin 1, and the one side portion 2 b is on the fin 1. It is located on the open end 5a side of the formed tube insertion portion 5.
The distance in the gravity direction between the heat transfer tubes 2 adjacent to each other in the vertical direction is constant at the pitch P2 of the tube insertion portions 5 adjacent to the fins 1.
The heat transfer tube 2 is made of, for example, aluminum or aluminum alloy.

  A plurality of partition walls 2A are formed inside the heat transfer tube 2, and a plurality of refrigerant channels 20 are formed inside the heat transfer tube 2 by the partition walls 2A. A groove or a slit may be formed on the surface of the partition wall 2 </ b> A and the inner wall surface of the heat transfer tube 2. Thereby, a contact area with the refrigerant | coolant which flows through the refrigerant | coolant flow path 20 will increase, and heat exchange efficiency will improve.

The heat transfer tube 2 is formed so that the upper surface 2a and the lower surface 2c are substantially symmetric with respect to a vertical line passing through the center portion in the width direction. Thereby, it becomes easy to ensure the manufacturability when the heat transfer tube 2 is extruded.
In addition, after producing the heat exchanger tube 2 so that a cross section may become an ellipse shape by extrusion molding, you may form the final shape by an additional process, for example.

(Detailed configuration of fin 1)
FIG. 5 is a side view showing a state of the heat exchanger 150 as viewed from another direction. FIG. 6 is a configuration diagram illustrating an example of a specific configuration example of the fins 1 constituting the heat exchanger 150. Based on FIG.5 and FIG.6, one of the specific structural examples of the fin 1 is demonstrated in detail. FIG. 5 schematically shows a portion where the number of fins 1 is six and the number of heat transfer tubes 2 is three. Moreover, in FIG. 6, the part in which the eight pipe | tube insertion parts 5 are formed is shown.

  6 is referred to as the longitudinal direction of the fin 1, and the insertion direction of the heat transfer tube 2 with respect to the fin 1 is referred to as the short direction of the fin 1. Note that the short direction of the fin 1 may be referred to as the width direction of the fin 1. These definitions will be used in the following description as well.

  As shown in FIGS. 5 and 6, the fin 1 is composed of a plate-like member having a longitudinal direction and a short direction. The fin 1 has a plurality of tube insertion portions 5 arranged at intervals in the longitudinal direction. The tube insertion portion 5 is formed with an opening so that one side of the fin 1 is released and extends in the short direction of the fin 1. In FIG. 6, one end portion side of the tube insertion portion 5 is illustrated as a release end portion 5a, and the other side portion side is illustrated as a back portion 5b. Further, as shown in FIG. 6, positioning holes 21 are formed in the fin 1 at two upper and lower positions. The fin 1 is made of, for example, aluminum or aluminum alloy.

  The tube insertion part 5 has a semicircular back part 5b. The shape of the back portion 5b is not limited to a semicircular shape, and may be an ellipse. That is, the back portion 5b may be formed in a shape corresponding to the shape of the other side portion 2d of the heat transfer tube 2 inserted into the tube insertion portion 5.

  Moreover, the fin 1 is comprised by the waveform shape which has the peak part and the trough part. The corrugation is formed with respect to the longitudinal direction of the plate-like member constituting the fin 1. That is, the fin 1 is configured in a corrugated shape such that the peaks and valleys extend in the short direction of the fin 1. Specifically, the fin 1 is configured such that the ridge line of the corrugated peak portion extends in the width of the fin 1. By having the corrugated shape in part, the fin 1 can be expanded and contracted in the longitudinal direction.

  Furthermore, the tube insertion part 5 is formed in the corrugated peak part and trough part of the fin 1. That is, the heat transfer tubes 2 are attached to the wave-shaped peaks and valleys of the fins 1. Further, it is desirable that the corrugated pitch of the fin 1 is equal to twice the pitch P2. The pitch of the corrugated shape of the fin 1 is the distance from the peak (or valley) constituting the corrugated shape to the peak (or valley).

  Note that the number of corrugations is not particularly limited, and may be formed according to the number of heat transfer tubes 2 to be mounted. In addition, the shape of the peak of the corrugated peak and valley is not particularly limited, and may be configured with an angle, or may be configured with a curved surface as the R portion. Furthermore, the angles of the peaks of the corrugated peaks and valleys are not particularly limited. Furthermore, it is not necessary that the ridge line of the corrugated peak portion is strictly parallel to the short direction of the fin 1.

(Manufacturing process of heat exchanger 150)
Here, the manufacturing process of the heat exchanger 150 will be described.
First, the fin 1 in which the tube insertion part 5 in which the heat transfer tube 2 can be inserted from one side is formed. A heat transfer tube 2 to be attached to the tube insertion portion 5 of the fin 1 is prepared. Then, the heat transfer tube 2 is inserted into the tube insertion portion 5 of the fin 1. When the heat transfer tube 2 is inserted into the tube insertion portion 5, the heat transfer tube 2 and the fin 1 are fixed. For example, the heat transfer tube 2 and the fin 1 can be fixed by a method such as brazing or bonding.

  Both ends of the heat transfer tube 2 are provided with a header (for example, the windward header collecting tube 153 and the leeward header collecting tube 154 shown in FIG. 2) and a connection member (for example, the inter-row connecting member 155 shown in FIG. 2). (See the white arrow shown in FIG. 2). Both ends of the heat transfer tube 2 inserted in these are fixed by brazing, for example.

  Thus, the heat exchanger 150 is assembled by a manufacturing process in which the fins 1 are first attached to the heat transfer tubes 2 and then the headers are attached. That is, since the pitch of the heat transfer tubes 2 adjacent to each other in the upper and lower directions is regulated by the pitch P2 of the tube insertion portion 5 of the fin 1 that has been previously attached, the heat transfer tube attachment portion (for example, FIG. The position of the heat transfer tube 2 and the position of the heat transfer tube mounting portion formed in the header are shifted due to the position tolerance of the tube mounting portion 153a and the tube mounting portion 154a) shown in FIG. there is a possibility.

  Therefore, in the heat exchanger 150, the fin 1 configured in a wave shape is employed. The fin 1 configured in a corrugated shape is more flexible than the fin configured by a flat plate member, and is easily stretched and deformed. Therefore, the pitch P2 of the tube insertion portion 5 of the fin 1 can be adjusted according to the pitch P1 of the heat transfer tube mounting portion of the header. That is, when the fin 1 expands and contracts in the longitudinal direction, the pitch P2 of the tube insertion portion 5 of the fin 1 can be matched with the pitch P1 of the heat transfer tube mounting portion of the header.

  Therefore, when the heat transfer tube 2 to which the fin 1 is attached is inserted into the header, the pitch P2 of the tube insertion portion 5 of the fin 1 can be adjusted to correspond to the pitch P1 of the heat transfer tube attachment portion of the header. Therefore, the deviation between the pitch P1 and the pitch P2 can be automatically corrected by the fin 1, and the assemblability of the heat exchanger 150 can be improved.

  Further, since the heat transfer tubes 2 are attached to the corrugated peaks and valleys of the fin 1, even if the fin 1 is deformed and the pitch P2 of the tube insertion portion 5 changes, the tube of the fin 1 The insertion portion 5 is kept perpendicular to the heat transfer tube 2. Therefore, it can suppress that the fin 1 inclines (bends) with respect to the heat exchanger tube 2, or becomes a heat exchanger tube insertion defect by inclining.

In addition, even if it is the construction method which attaches the heat exchanger tube 2 to a header first and inserts the heat exchanger tube 2 in the fin 1 after that, there exists the same effect.
Moreover, although the case where the whole longitudinal direction of the fin 1 was corrugated was demonstrated to the example, it is not limited to this, At least one part of the fin 1 should just be corrugated. The range of the corrugated shape may be determined in consideration of the assumed gap between the pitch P1 and the pitch P2.
Further, it is not necessary to make the entire fin 1 corrugated, and it is sufficient that at least one fin 1 has a corrugated shape. However, it is preferable that the fins 1 have a corrugated shape, preferably at the rate of the whole of the fins 1 or some of the fins. The same applies to other configurations of the fin 1 described below.

(Detailed configuration of fin 1 part 2)
FIG. 7 is a side view showing a state in which another example of the configuration of the heat exchanger 150 is viewed from another direction. FIG. 8 is a configuration diagram showing another example of a specific configuration example of the fins 1 constituting the heat exchanger 150. Based on FIG.7 and FIG.8, one of the specific structural examples of the fin 1 is demonstrated in detail. In FIG. 7, a portion in which the number of fins 1 is 6 and the number of heat transfer tubes 2 is 3 is schematically illustrated. Moreover, in FIG. 8, the part in which the eight pipe | tube insertion parts 5 are formed is shown.

  5 and 6 show an example in which the tube insertion portion 5 is formed in the corrugated peaks and valleys of the fin 1, but in FIGS. 7 and 8, the tube insertion portion 5 is the fin 1. The example which is formed in either the peak part or trough part of a corrugated shape is shown. Other configurations are basically the same as those described with reference to FIGS. That is, the corrugated pitch of the fin 1 is set equal to the pitch P2.

  Even with such a configuration, the fin 1 can be expanded and contracted in the longitudinal direction, and the deviation between the pitch P1 and the pitch P2 can be automatically corrected by the fin 1. Therefore, the assemblability of the heat exchanger 150 can be improved, and the fin 1 can be tilted (bent) with respect to the heat transfer tube 2 and the heat transfer tube insertion failure due to the tilt can be suppressed.

  Further, in the fin 1 in which the tube insertion portion 5 is formed in either the wave-shaped peak portion or valley portion of the fin 1, even if the fin 1 is deformed and the pitch P2 of the tube insertion portion 5 changes, the fin 1 The wave shape between the tube insertion portions 5 adjacent to the upper and lower sides of 1 moves in the fin pitch direction. Therefore, the attachment part of the heat exchanger tube 2 and the fin 1 does not move in the fin pitch direction, and the fin pitch is stabilized. The fin pitch is a distance between the fin 1 and the fin 1.

(Detailed configuration of fin 1 3)
FIG. 9 is a side view showing another example of the configuration of the heat exchanger 150 as seen from another direction. FIG. 10 is a configuration diagram showing another example of a specific configuration example of the fin 1 constituting the heat exchanger 150. One specific configuration example of the fin 1 will be described in detail with reference to FIGS. 9 and 10. FIG. 9 schematically shows a portion where the number of fins 1 is six and the number of heat transfer tubes 2 is three. Moreover, in FIG. 10, the part in which the eight pipe | tube insertion parts 5 are formed is shown.

  5 to 8 show an example in which the entire longitudinal direction of the fin 1 has a corrugated shape, but in FIG. 9 and FIG. 10, the corrugated shape is formed on a part of the fin 1. An example is shown. Specifically, a corrugated shape having a pitch smaller than the pitch P <b> 2 of the tube insertion portion 5 of the fin 1 is formed in a part of the fin 1. 9 and 10 show an example in which the corrugated shape is formed between the positioning hole 21 and the tube insertion portion 5 adjacent to the positioning hole 21. Other configurations are basically the same as those described with reference to FIGS.

  Even with such a configuration, the fin 1 can be expanded and contracted in the longitudinal direction, and the deviation between the pitch P1 and the pitch P2 can be automatically corrected by the fin 1. Therefore, the assemblability of the heat exchanger 150 can be improved, and the fins 1 can be tilted (bent) with respect to the heat transfer tube 2, and the heat transfer tube insertion failure due to the tilt can be suppressed.

  Usually, the fin 1 is often formed with a pattern such as a scratch or a slit. In that case, it is preferable that the formation surface of the fin 1 is a flat surface because the shape is stabilized. Accordingly, in FIG. 9 and FIG. 10, the corrugated shape is formed in part. Therefore, the fin 1 is concentrated and deformed in a corrugated shape, and portions other than the corrugated shape can be left flat. Therefore, formation of patterns such as scratches or slits can be stabilized. 9 and 10 show an example in which the corrugated shape is formed between the positioning hole 21 and the tube insertion portion 5 adjacent to the positioning hole 21. The formation position is not limited to this position.

(Mounting of heat transfer tube 2 to fin 1)
In the heat exchanger 150, the heat transfer tubes 2 and the fins 1 are joined by an interference fit.

  Usually, the fin does not have a function of automatically adjusting the pitch deviation. For this reason, if the gap between the heat transfer tube and the fin tube insertion portion is reduced, the portion of the fin that interferes with the heat transfer tube is deformed, making it difficult to attach the heat transfer tube. Therefore, in the conventional heat exchanger, the gap between the heat transfer tube and the fin tube insertion portion cannot be reduced, and the heat transfer tube is not attached to the fin using an interference fit.

  On the other hand, since the heat exchanger 150 has the fin 1 having the shape shown in FIGS. 5 to 10, since the pitch shift is automatically adjusted, the gap between the two can be minimized. That is, the heat exchanger 150 is not intended to eliminate the pitch deviation due to the gap between the heat transfer tube 2 and the tube insertion portion 5 of the fin 1, and therefore, the heat exchanger 150 uses an interference fit with a small gap between the two. It becomes possible to attach the heat tube 2 to the fin 1. By attaching the heat transfer tube 2 to the fin 1 using an interference fit, it is possible to improve brazing and adhesion, and to reduce the amount of wax used.

  As described above, in the heat exchanger 150, since the fin 1 has a shape capable of automatically adjusting the pitch shift, the pitch P2 of the tube insertion portion 5 of the fin 1 is changed to the pitch P1 of the heat transfer tube mounting portion of the header. It can be adjusted to correspond. Therefore, according to the heat exchanger 150, there is no gap between the pitch P2 of the tube insertion portion 5 of the fin 1 and the pitch P1 of the heat transfer tube mounting portion of the header, and the assemblability is improved.

  In addition, since the air conditioner 100 according to Embodiment 1 applies at least one of the first heat exchanger 102 and the second heat exchanger 104 as the heat exchanger 150, the amount of assembly is increased accordingly. Will be improved.

  Although the heat exchanger according to the present invention has been described based on some detailed configurations, the present invention is not limited thereto, and various modifications and changes can be made without departing from the scope and spirit of the present invention. Moreover, although the heat exchanger provided with the several fin 1 was demonstrated to the example, it is not limited to this, The fin 1 may be one.

  1 fin, 2 heat transfer tube, 2A partition, 2a upper surface, 2b one side, 2c lower surface, 2d other side, 5 tube insertion portion, 5a open end, 5b back, 20 refrigerant flow path, 21 positioning hole, 100 Air conditioner, 101 compressor, 102 1st heat exchanger, 103 throttle device, 104 2nd heat exchanger, 105 1st fan, 106 2nd fan, 107 flow path switching device, 110 refrigerant piping, 150 heat exchanger , 151 leeward side heat exchanger, 152 leeward side heat exchanger, 153 leeward side header collecting pipe, 153a pipe mounting part, 154 leeward side header collecting pipe, 154a pipe mounting part, 155 inter-row connecting member, P1 pitch (header Pitch of heat transfer tube mounting portion), P2 pitch (pitch of fin tube insertion portion).

The heat exchanger according to the present invention includes a plate-shaped fin, a plurality of heat transfer tubes attached to a tube insertion portion formed in the fin so as to intersect the fin, and an end portion of the heat transfer tube is a heat transfer tube A header inserted into the mounting portion, and the heat transfer tubes are arranged at intervals in the long side direction of the fins, and the fins are at least partially corrugated, and the tubes of the fins The insertion portion is extendable in the long side direction so that the pitch of the insertion portion matches the pitch of the heat transfer tube mounting portion of the header .

Claims (9)

A plate-like fin, and a plurality of heat transfer tubes mounted so as to intersect the fin,
The heat transfer tubes are arranged at intervals in the long side direction of the fins,
The fin is
A heat exchanger having at least a part of a corrugated shape and capable of extending and contracting in the long side direction. The corrugated shape is
The heat exchanger according to claim 1, wherein a peak portion and a valley portion constituting the corrugated shape are formed to extend in a short side direction. The pitch of the corrugated shape is
The heat exchanger according to claim 1 or 2, wherein the pitch of the tube insertion portion formed in the fin is twice the pitch. The pitch of the corrugated shape is
The heat exchanger according to claim 1 or 2, wherein the pitch is the same as a pitch of tube insertion portions formed in the fin. The tube insertion part is
The heat exchanger according to claim 3 or 4, wherein the heat exchanger is formed at an apex portion of the corrugated shape. The pitch of the corrugated shape is
The heat exchanger according to claim 1 or 2, wherein the pitch is smaller than a pitch of tube insertion portions formed in the fin. The corrugated shape is
The heat exchanger according to claim 6, wherein the heat exchanger is formed between a positioning hole formed in the fin and the tube insertion portion adjacent to the positioning hole. The heat transfer tube is
The heat exchanger according to any one of claims 1 to 7, wherein the heat exchanger is joined to the fin by an interference fit. A refrigerant circuit in which a compressor, a first heat exchanger, an expansion device, and a second heat exchanger are connected by refrigerant piping;
A refrigeration cycle apparatus using the heat exchanger according to any one of claims 1 to 8 as at least one of the first heat exchanger and the second heat exchanger.

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